US11041489B2 - Compressor assembly for operating a compressed air supply system, compressed air supply system, and vehicle - Google Patents

Compressor assembly for operating a compressed air supply system, compressed air supply system, and vehicle Download PDF

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Publication number
US11041489B2
US11041489B2 US16/757,773 US201816757773A US11041489B2 US 11041489 B2 US11041489 B2 US 11041489B2 US 201816757773 A US201816757773 A US 201816757773A US 11041489 B2 US11041489 B2 US 11041489B2
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Prior art keywords
bearing
outer rotor
drive housing
arrangement
rotor
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US20200378377A1 (en
Inventor
Dirk Kirchhoff
Frank Meissner
Eduard Nuss
Marco Seeger
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ZF CV Systems Europe BV
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ZF CV Systems Hannover GmbH
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T17/00—Component parts, details, or accessories of power brake systems not covered by groups B60T8/00, B60T13/00 or B60T15/00, or presenting other characteristic features
    • B60T17/02—Arrangements of pumps or compressors, or control devices therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0094—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 crankshaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/121—Casings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/128—Crankcases
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/16—Filtration; Moisture separation
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K1/00—Details of the magnetic circuit
    • H02K1/06—Details of the magnetic circuit characterised by the shape, form or construction
    • H02K1/22—Rotating parts of the magnetic circuit
    • H02K1/27—Rotor cores with permanent magnets
    • H02K1/2786—Outer rotors
    • H02K1/2787—Outer rotors the magnetisation axis of the magnets being perpendicular to the rotor axis
    • H02K1/2788—Outer rotors the magnetisation axis of the magnets being perpendicular to the rotor axis the rotor consisting of a single magnet or two or more axially juxtaposed single magnets
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K5/00—Casings; Enclosures; Supports
    • H02K5/04—Casings or enclosures characterised by the shape, form or construction thereof
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/02—Additional mass for increasing inertia, e.g. flywheels
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/08—Structural association with bearings
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/08—Structural association with bearings
    • H02K7/086—Structural association with bearings radially supporting the rotor around a fixed spindle; radially supporting the rotor directly
    • H02K7/088—Structural association with bearings radially supporting the rotor around a fixed spindle; radially supporting the rotor directly radially supporting the rotor directly
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/14—Structural association with mechanical loads, e.g. with hand-held machine tools or fans

Definitions

  • the invention relates to a compressor arrangement including an external rotor electric motor arranged inside a drive housing and further including a pneumatic compressor.
  • Such a compressor arrangement for operating a compressed air supply installation has: an electric motor which is arranged inside a drive housing and which has an internal stator and an external outer rotor, wherein the outer rotor is arranged in a rotatable manner about the internal stator, and a pneumatic compressor.
  • Air supply installations in particular compressed air supply installations, for pneumatic suspensions, level adjustment systems or other applications are generally known.
  • Such air supply installations produce compressed air in order to supply compressed air consumers therewith, such as the pneumatic suspension mentioned by way of example.
  • the compressed air is produced by means of a compressor which is driven in particular via an electric motor.
  • WO 2009/033556 A1 discloses a compact dry-running piston compressor having at least one cylinder for compressing air by means of an associated piston which can be moved by electric motor by a crank mechanism which comprises a crankshaft and connecting rod and which is rotatably supported in an oil-bath-free compressor housing via permanently lubricated roller bearings and which produces a housing-internal cooling air flow as a result of the movement cycle, wherein the compressor housing comprises two housing halves which are separated via a partition wall in order to receive the crank mechanism within the first housing half and to receive the electric motor within the second housing half, wherein a roller bearing which is common to the crank mechanism and the electric motor and which is located in the cooling air flow which passes the first housing half is inserted in the partition wall.
  • DE 10 2013 003 513 A1 discloses a compressor arrangement which is mentioned in the introduction for operating a compressed air supply installation of a vehicle, having a compressor with an electric motor which is formed as an electronically commutated, brushless direct-current motor having a control circuit comprising an electronic power unit (BL-DC motor) and a pneumatic compressor. There is further provision for the electric motor to be formed in the form of an external rotor motor.
  • the present invention provides a compressor arrangement for operating a compressed air supply installation.
  • the compressor arrangement includes a pneumatic compressor and an electric motor arranged inside a drive housing, the electric motor having an internal stator and an external outer rotor.
  • the external outer rotor is arranged in a rotatable manner about the internal stator.
  • the external outer rotor is supported in a rotatable manner about a center axis with respect to the drive housing via a bearing arrangement.
  • the bearing arrangement has at least one bearing.
  • the external outer rotor is supported by the bearing arrangement on an outer circumference of the outer rotor.
  • FIG. 1 shows a constructive configuration of a compressed air supply installation
  • FIGS. 2A-F show different embodiments of a rotor bearing
  • FIGS. 3A-B are detailed views of an electric motor
  • FIG. 4 is a highly simplified schematic overview of a compressed air supply installation
  • FIG. 5 is a schematic illustration of a vehicle having a compressed air supply installation.
  • the present disclosure describes improved compressed air supply installations which partially or completely achieve such improved function.
  • the compressed air supply installations reduce the structural space and weight of a compressor arrangement, in particular a drive for a compressor, and improve the operating properties of a compressor.
  • the present disclosure describes a compressor arrangement for operating a compressed air supply installation having an electric motor which is arranged inside a drive housing and which has an internal stator and an external outer rotor, wherein the outer rotor is arranged in a rotatable manner about the internal stator, and a pneumatic compressor.
  • the outer rotor On the basis of this compressor arrangement, there is provision for the outer rotor to be supported in a rotatable manner about a center axis with respect to the drive housing via a bearing arrangement which has at least one bearing, and for the outer rotor to be supported, in particular exclusively, by the bearing arrangement on the outer circumference of the outer rotor.
  • the disclosure takes as a basis the consideration that an external rotor motor acting as a drive motor for a compressor generally leads to advantages. These advantages include in particular the additional property of the outer rotor as a flywheel for storing energy and the moment of inertia which can be achieved in connection with a brushless direct-current motor and the consequently higher dynamic requirements which can be achieved. It is also possible by means of a constructional configuration of the electric motor in the form of an external rotor motor to achieve a considerable reduction of the installation space and consequently the spatial requirements and weight requirements of the entire compressed air supply installation.
  • the disclosure has recognized that support of the outer rotor, in particular the external rotor, on the outer circumference leads to advantages. These advantages include the additional shielding from electromagnetic radiation as a result of the bearing which is located outside the rotor bell-like member. Radiation emitted by the electric motor is thus shielded in an improved manner and the electromagnetic compatibility of the compressor arrangement is increased in a positive manner.
  • stator it may advantageously be possible, as a result of the support on the outer circumference of the outer rotor, for the magnetic flux in the stator to be improved because, in comparison with other known active principles, no opening in the stator is required to introduce the motor shaft.
  • the active diameter of the rotor bell-like member is influenced to a lesser extent as a result of external forces, in particular connecting rod forces. Therefore, the air gap of the motor can be advantageously reduced as a result of a constructional configuration.
  • the outer rotor can have a flywheel mass weight.
  • the outer rotor prefferably has a practically cylindrical eccentric journal which is arranged about an eccentric axis E, wherein the eccentric axis E is arranged parallel, but with a lifting spacing H relative to the center axis M, in particular the eccentric journal is formed in the form of a formation on a rotor end portion for receiving a connecting rod via a connecting rod bearing.
  • this means that the eccentric journal which is used to rotatably connect the outer rotor to the connecting rod is arranged directly on the outer rotor, in particular on the rotor end portion.
  • the drive housing to have a drive housing body and a drive housing cover, wherein the stator is retained on the drive housing cover and the outer rotor is supported at an inner side of a housing wall of the drive housing body.
  • this may mean in particular that the stator is arranged on the drive housing cover and consequently the assembly of the electric motor is carried out practically by the insertion of the drive housing cover in the drive housing.
  • the drive housing body to integrally form a motor housing and a crankcase of the compressor.
  • the drive housing cover is positioned on a front opening of the drive housing body in a closing manner at the front side.
  • the drive housing cover and the drive housing body can be constructed by mutually conformed fitting faces in an axial and radial direction in a self-centering manner in order to form a common stator and rotor axis.
  • the drive housing cover is orientated relative to the drive housing body and consequently in particular the stator is orientated relative to the outer rotor.
  • the assembly and maintenance-friendliness of the drive of the compressor arrangement can advantageously be improved because the orientation of the stator relative to the outer rotor no longer has to be provided by corresponding fixing elements or adjustment steps during the assembly.
  • stator in the context of a preferred development, there is provision for the stator to be arranged in such a manner that the axis of symmetry of the stator is orientated coaxially with the center axis, in particular the axis of symmetry of the stator is located on the center axis.
  • a drive shaft as used in conventional compressor drives can be dispensed with.
  • the outer rotor as a self-carrying unit, that is to say, a unit which transmits drive forces or torques directly and without any drive shaft.
  • the region of the stator surrounding the center axis it is advantageously possible for the region of the stator surrounding the center axis to be constructed in a materially filling manner, in particular without any opening for a rotor shaft.
  • the region around the rotation axis of the outer rotor which would normally be provided for an opening for introducing a motor shaft can be constructed in a materially filling manner.
  • the magnetic flux in the stator is advantageously improved.
  • the plate assembly of the stator may be at least partially constructed in a non-materially filling manner and therefore at least partially in a hollow manner. This may be advantageous, for example, in order to achieve weight savings.
  • the bearing arrangement to have a bearing without an inner ring or a bearing without an outer ring.
  • a bearing without an inner ring means that the bearing does not have any inner ring.
  • the outer rotor of the electric motor, in particular the rotor bell-like member performs the function of the inner bearing ring, of at least one bearing of the bearing arrangement.
  • the outer rotor, without a bearing inner ring being positioned is in direct contact with the roller bearings or, in the case of a sliding bearing, in direct contact with the bearing outer ring.
  • a bearing without an outer ring means that the bearing does not have an outer ring.
  • portions of the inner side of the housing wall which form a running face for the roller members perform the function of the bearing outer ring of at least one bearing of the bearing arrangement.
  • the surfaces which perform the function of the respective bearing rings can be produced in such a manner that they have, for example, as a result of suitable processing, surface and shape properties which qualify the outer rotor for use as a bearing inner ring or bearing outer ring.
  • processing may particularly have pretreatment steps in order to adjust, in particular to increase, hardness and strength parameters of the surface which is in contact with the roller members, in particular the outer surface of the rotor bell-like member or the inner side of the housing wall, in particular in order to bring about operation of the drive with little noise and wear.
  • the electric motor is formed as an electronically commutated, brushless direct-current motor having a control circuit comprising an electronic power unit.
  • the electric motor can be constructed according to these two structural forms, in accordance with constructive requirements. These requirements include in particular the price, dynamic properties during operation, such as acceleration, torque, speed and furthermore electromagnetic compatibility, service-life and freedom from maintenance.
  • the bearing is selected from a group of bearings comprising: sliding bearings, needle bearings, ball bearings, spherical roller bearings and cylindrical roller bearings.
  • Needle and cylindrical roller bearings and generally roller bearings with cylindrical roller members have, as a result of the linear contact with the running face, a generally high radial load-bearing capacity.
  • needle bearing in addition it is relatively compact as a result of the small roller member diameter and consequently in an advantageous manner it further reduces the installation space of the drive.
  • ball bearings have a relatively high axial and radial load-bearing capacity.
  • Spherical roller bearings further allow, as a result of the spherical configuration of the roller members and a hollow-sphere-like outer ring ball race, a specific oscillating movement between the inner ring and outer ring. Consequently, non-sensitivity with respect to oblique positioning and alignment errors of the rotor with respect to the stator are achieved.
  • the bearing arrangement is advantageously provision for the bearing arrangement to have at least one single-rowed bearing or at least one multi-rowed bearing. This may involve in specific terms the outer rotor being formed by means of a two-rowed deep-groove ball bearing or two-rowed oblique ball bearing.
  • a multi-rowed arrangement advantageously leads to an increase of the load-bearing capacity and allows, particularly with the oblique ball bearing, the adjustment of different pressure angles. Furthermore, as a result of the arrangement of the oblique bearing rows, freedom from play, support width, axial load-bearing capacity and axial force transmission can be influenced in order to comply with constructive requirements.
  • the outer rotor is constructed in order to be fixed by the magnetic forces acting in the electric motor in an axial direction.
  • the structure-borne noise transmission from the outer rotor to the stator and therefore to the drive housing is also reduced, which has an advantageous effect on vibrations and noise development.
  • the risk of damage to the bearing or bearing fixing is reduced by axial forces from the crank mechanism which act in an axial direction and which in particular pulse in an abrupt manner, not being transmitted directly into the bearing and therefore into the entire unit.
  • the outer rotor in an axial direction.
  • This may involve in specific terms the fact that the bearing for supporting the rotor on the outer circumference is constructed to receive axial forces.
  • this may mean that the fixing is carried out in an axial direction via a second bearing which is arranged with an axial spacing from the first bearing.
  • This bearing can be constructed as a radial bearing which receives axial forces or as an exclusively axial bearing.
  • At least one weight in particular a flywheel mass weight and/or a compensating weight for compensating for imbalance, to be arranged on the circumference of the rotor, in particular on the circumference of the rotor bell-like member.
  • This particularly relates to forces which are directed into the outer rotor as a result of the eccentric journal and components fixed thereto. In this manner, a low-vibration and low-noise operation of the drive and consequently of the compressor is advantageously achieved. In particular, a complete rotational mass compensation is achieved.
  • the outer rotor is rotatably supported on the drive housing by means of two bearings which are arranged with spacing in an axial direction.
  • the support width of the bearing can be increased by the two-fold bearing arrangement, in particular for receiving bending moments in an improved manner.
  • the stator in an axial direction so as to be adjustable on the drive housing cover.
  • This adjustability can be achieved in constructive terms, for example, by an adjustment thread in the stator or a drive housing cover which is adjustable in an axial direction.
  • slots can be provided in the drive housing body in an axial direction.
  • the drive housing cover can be fixed, for example, by means of screws after adjustment of the desired axial position.
  • the drive housing body can be constructed in such a manner that it has at least one groove which extends helically on a cylindrical inner surface of the opening for the drive housing cover.
  • FIG. 1 shows a constructive configuration of a compressed air supply installation 1000 in the context of a first variant of a particularly preferred embodiment.
  • the compressed air supply installation 1000 has a housing 120 which in turn has a dryer and valve housing 122 , a compressor housing 124 and a drive housing 126 .
  • the housing 120 thereof can be seen with a drive housing 126 for carrying out the compressor arrangement 100 comprising the compressor 400 and the drive, wherein the drive in the form of an electric motor 300 and the crank mechanism 350 are received in the drive housing 126 .
  • the drive housing can equally well be configured as a motor housing or a similar housing.
  • the housing arrangement 120 further comprises a compressor housing 124 for the compressor 400 .
  • a dryer and valve housing 122 adjoins the compressor housing 124 and comprises the dryer housing and electric and/or electronic and pneumatic interfaces together with a mechatronic system and an arrangement of valves—substantially to illustrate the valve arrangement 142 .
  • the connecting rod 404 which is itself configured as a piston rod is supported on an eccentric journal 342 .
  • the drive formed with the electric motor 300 for the crank mechanism 350 and the crank mechanism 350 are substantially received in the drive housing 126 .
  • the drive itself has a stator 304 with a stator winding 306 in order to form the electric motor 300 .
  • the drive has a rotor or outer rotor 340 having a rotor bell-like member 348 and an arrangement of permanent magnets 308 fitted thereto.
  • the outer rotor 340 is retained separately by an air gap 312 around the stator 304 .
  • the stator 304 is consequently surrounded by the outer rotor 340 in a rotatable manner about a center axis M which coincides with the axis of symmetry S of the stator 304 by the stator 304 being arranged accordingly.
  • the outer rotor 340 is rotatably retained on a bearing arrangement 320 in the drive housing 126 , that is to say, in an inner side 132 of a housing wall 129 of the drive housing 126 , while the stator 304 is formed as part of a drive housing cover 130 .
  • the drive housing 126 can be closed by means of the drive housing cover 130 by inserting the drive housing cover 130 into a front opening 134 of the drive housing body 128 .
  • the stator 304 can also be releasably fixed on the drive housing cover 130 via suitable fixing means, in particular screws.
  • the outer rotor 340 can be fixed via the magnetic forces MK which act in the electric motor 300 and which are schematically indicated here in an axial direction A.
  • adjustment means for example, one or more threads or one or more fitting faces which allow an axial displaceability of the drive housing cover 130 relative to the drive housing body 128 .
  • adjustment screws can also be used to adjust and fix the drive housing cover or the stator.
  • the outer rotor 340 does not have any central rotor shaft in the conventional sense but instead forms with the rotor bell-like member 348 a self-supporting, in particular integral, unit, on which the eccentric journal 342 which is particularly formed by an integral formation 341 is also fixed.
  • the outer rotor 340 and the eccentric journal 342 and the connecting rod 404 form the significant force-transmitting elements of the crank mechanism 350 which is driven by the electric motor 300 , wherein the connecting rod 404 is connected to the eccentric journal 342 in a rotationally movable manner by means of a connecting rod bearing 344 .
  • the connecting rod bearing 344 is constructed to carry out a rotating movement of the rotor 340 and, in an additional configuration, also a back and forth movement of the connecting rod 404 .
  • the connecting rod 404 and accordingly the piston 402 is caused to carry out a mainly translational lifting movement for driving the compressor.
  • the outer rotor may have a compensation weight for compensating for the imbalance brought about by the eccentric journal 342 and components fixed thereto, which is not illustrated in greater detail here.
  • FIGS. 2A to 2F illustrate as a cross-sectional cutout by way of example different embodiments of the bearing 320 of the rotor 340 .
  • the cutout shows a cross-section through the bearing ring at the transition between the rotor bell-like member 348 and the drive housing body 128 .
  • FIG. 2A schematically shows a cutout of the rotor bearing.
  • a bearing arrangement 320 a has a bearing 313 a in the form of a sliding bearing 314 which allows a rotating relative movement between the rotor bell-like member 348 of the outer rotor 340 and the drive housing body 128 .
  • the advantage of a sliding bearing involves the small constructive complexity by means of which the bearing can be produced.
  • an axial movability of the rotor is provided and is limited only by other forces which act on the outer rotor 340 , for example, of the stator 304 or the connecting rod 404 .
  • the sliding bearing can further be produced using different construction methods, for example, by a sliding sleeve which is formed from a low-friction material or in the form of a hydrodynamic sliding bearing. For the last case, however, constructive measures for shielding and storing a lubricant would again have to be carried out and increase the construction complexity.
  • FIG. 2B further shows a cutout I of an additional embodiment of the rotor bearing.
  • a bearing arrangement 320 b has a bearing 313 b without an inner ring in the form of a needle bearing 315 without an inner ring, that is to say that the needle bearing 315 without an inner ring does not have any bearing inner ring but instead the roller members 322 b are in direct contact with the outer surface of the rotor bell-like member 348 .
  • An outer ring 324 b of the needle bearing 315 further has at the left side and the right side thereof an edge B, which limits the movement of the roller members 322 b in an axial direction.
  • the surface of the rotor bell-like member 348 is constructed in such a manner that it can be moved in an axial direction relative to the roller members 322 b and therefore the needle bearing 315 without an inner ring is formed as a movable bearing. In a manner similar to the embodiment shown in FIG. 2A , this results in an axial movability of the rotor 340 which is limited only by the already-described additional forces which act on the outer rotor 340 .
  • the embodiment shown in FIG. 2B has a particularly advantageous effect on the necessary structural space as a result of the compact construction type, particularly as a result of the small roller member diameter and the omitted bearing inner ring.
  • a bearing arrangement 320 b ′ which is shown in an additional view II to provide, with a bearing 313 b ′ which does not have an outer ring, an arrangement which is transposed in a radial direction of the bearing elements described here.
  • roller members 322 b ′ are in direct contact with the inner side 132 of the drive housing body 128 .
  • a bearing inner ring 326 b ′ has, similarly to the above-described outer ring 324 b , at the left side and right side thereof an edge B′, which limits the movement of the roller members 322 b ′ in an axial direction. Consequently, the above-described advantages are similarly achieved, with particular regard to the structural space.
  • FIG. 2C shows a cutout of an additional preferred development of a rotor bearing.
  • the rotor bell-like member 348 is rotatably supported in the drive housing body 128 via a bearing arrangement 320 c which is constructed with a bearing 313 c in the form of a needle bearing 316 with an inner ring.
  • the bearing 316 has both a bearing outer ring 324 c and a bearing inner ring 326 c .
  • both the bearing outer ring 324 c and the bearing inner ring 326 c have at the left side and right side edges B which limit the movement freedom of the rolling members 322 c in an axial direction and thus allow the transmission of axial forces by the bearing arrangement 320 c .
  • the outer rotor 340 or the rotor bell-like member 348 is retained via the bearing arrangement 320 c axially in the drive housing body 128 .
  • forces which act in an axial direction and which, for example, are directed via the connecting rod into the outer rotor 340 can be taken up by the bearing arrangement 320 c and directed into the drive housing body 128 independently of the magnetic forces which act as a result of the electric motor 300 .
  • FIG. 2D shows an additional preferred embodiment of the rotor bearing.
  • a bearing arrangement 320 d has a bearing 313 d in the form of a multi-rowed rolling bearing 317 having a bearing outer ring 324 d and a bearing inner ring 326 d which is formed in this instance as a two-rowed deep-groove ball bearing 317 ′.
  • the two-rowed construction type also has a positive effect on the prevention of tilting of the rotor as a result of torques, in particular bending torques, which are introduced via connecting rod forces which act on the outer rotor 340 . It is further possible, instead of the two-rowed deep-groove ball bearing 317 ′, to use a one-rowed ball bearing 317 ′′, in particular a deep-groove ball bearing, which has only one row of roller members 322 d and which is not illustrated here.
  • FIG. 2E shows an additional preferred embodiment of the rotor bearing.
  • a bearing arrangement 320 e has a bearing 313 e in the form of a cylindrical roller bearing 318 .
  • the roller members 322 e of a cylindrical roller bearing 318 have a larger diameter.
  • both the bearing outer ring 324 e and the bearing inner ring 326 e also have edges B, which limit the axial freedom of movement of the roller members 322 e .
  • the outer rotor 340 is fixed by the bearing arrangement 320 e in the embodiment shown in FIG. 2E . It is also possible to use, instead of a cylindrical roller bearing 318 , a spherical roller bearing 319 which has sphere-like roller members in place of cylindrical roller members and which is not illustrated here.
  • FIG. 2F shows an additional particularly preferred embodiment of the rotor bearing.
  • a bearing arrangement 320 f has two separate roller bearings 313 , which are constructed in this instance as deep-groove ball bearings 317 , that is to say, a bearing 313 . 1 remote from the connecting rod and a bearing 313 . 2 near the connecting rod.
  • the bearing 313 . 1 remote from the connecting rod has a bearing outer ring 324 f . 1 and a bearing inner ring 326 f . 1 .
  • the bearing 313 . 2 near the connecting rod has a bearing outer ring 324 f . 2 and a bearing inner ring 326 f . 1 .
  • the bearings 313 . 1 , 313 . 2 are constructed in this development as a one-rowed deep-groove ball bearing 317 .
  • L which describes the axial spacing of both bearings 313 . 1 , 313 . 2
  • Such torques can be directed into the outer rotor 340 in particular in the form of connecting rod forces which act on the eccentric journal 342 .
  • the bearing types which are illustrated in FIGS. 2B, 2C, 2D and 2E in particular the bearing arrangements 320 b , 320 c , 320 d , 320 e , can be fixed in an axial direction in the drive housing in a positive-locking manner. This can be achieved in particular by a step on the fitting face which acts as a bearing seat in the drive housing body 128 , against which step the bearing outer ring 324 , 324 b , 324 c , 324 d , 324 e is pressed during assembly of the drive housing cover 130 by a suitable annular step in the drive housing cover 130 .
  • the bearings 313 b - e , 313 . 1 , 313 . 2 illustrated in FIGS. 2B, 2C, 2D, 2E and 2F in the bearing arrangements 320 b , 320 c , 320 d , 320 e , 320 f are all special construction forms of one or more roller bearings.
  • the individual bearing types can be varied depending on requirements and applications. Thus, for example, in place of the arrangement shown in FIG. 2F of two deep-groove ball bearings, two needle bearings or cylindrical roller bearings can also be used.
  • a spacer sleeve for fixing in an axial direction can further be used between the bearing outer rings of the individual bearings.
  • steps with different diameters can also be used both at the side of the rotor 340 and at the side of the drive housing body 128 in order to fix the respective bearing outer rings 324 f . 1 , 324 f . 2 and bearing inner rings 326 f . 1 , 326 f . 2 in a positive-locking manner in an axial direction.
  • bearings having different inner and outer diameters in order to be fixed in a positive-locking manner in an axial direction at different cylindrical steps with similarly different diameters.
  • FIG. 3A is a schematic view of an electric motor 300 ′ in another preferred development.
  • the stator 304 is arranged on the drive housing cover 130 .
  • the rotor bell-like member 348 ′ of the outer rotor 340 ′ is constructed and arranged in such a manner that it radially surrounds the stator 304 and is supported rotatably about the center axis M.
  • An illustration of details, in particular of the bearings, has been omitted for reasons of clarity and simplification.
  • the outer rotor 340 ′ further has on the rotor end portion 346 ′ an eccentric journal 342 in the form of an integral formation 341 , the eccentric axis E of which is arranged with radial lifting spacing H from the center axis M.
  • a flywheel mass weight 360 which is constructed in this development as an annular mass-encumbered member which in this instance constitutes practically an extension of the rotor bell-like member in an axial direction is arranged on the rotor end portion 346 ′.
  • a flywheel mass weight 360 is possible, for example, on the outer circumference 343 of the rotor bell-like member 348 ′ or on the inner circumference 345 , with an adequate axial spacing from the stator winding 306 , permanent magnet arrangement 308 and a bearing arrangement 320 , 320 a - f which is not illustrated here, and generally as the structural space of the development allows.
  • an electric motor 300 ′′ shown in FIG. 3B differs from the development shown in FIG. 3A in that it does not have any flywheel mass weight 360 but instead on the rotor end portion 346 ′′ a compensation weight 370 which is arranged in particular opposite the eccentric journal 342 in a radial direction in order to achieve a rotational mass compensation. It is thereby particularly intended to be possible for the mass and inertia forces of the eccentric journal 342 and the components which are connected to the eccentric journal 342 , in particular the connecting rod 404 , which is not illustrated here, and piston 402 to be compensated for by the accelerated compensation weight 370 . Thus, it may be possible in a constructive manner for occurring imbalances to be able to be minimized and in particular practically completely eliminated.
  • the compensation weight is fitted as close as possible to the outer circumference 343 of the rotor bell-like member 348 ′′ of the outer rotor 340 ′′ because it can thus advantageously be smaller in order to produce a force which compensates for the imbalances, in particular in comparison with an arrangement nearer the axis of symmetry S of the stator or rotor.
  • FIG. 4 is a highly simplified, schematic overview of a compressed air supply installation 1000 with a compressor arrangement 100 for supplying a pneumatic installation 600 .
  • the compressed air supply installation 1000 has an air intake 0 for drawing fresh air which is further connected to an inlet of the compressor 400 in a fluid-conveying, in particular gas-conveying manner.
  • the compressor 400 is driven as part of the compressor arrangement 100 by a drive 200 having an electric motor 300 which is constructed in this case as a brushless direct-current motor 301 and which is controlled by a control circuit 700 with an electronic power unit 701 , via an outer rotor 340 .
  • the compressed fresh air is further provided via a compressed air source 1 , to which a branch 510 is connected.
  • a ventilation 3 is connected to this branch 510 , on the one hand, via a ventilation valve 520 .
  • an air dryer 540 which further leads to a compressed air connection 2 is connected to the branch 510 .
  • a compressed air store 560 is connected thereto via a storage line 564 and a storage valve 562 and furthermore the pneumatic installation 600 is connected thereto via a screen 570 .
  • the pneumatic installation 600 may be, for example, a pneumatic spring installation or an additional pneumatic installation, in particular of a vehicle.
  • individual valves, throttles and similar adjustment means and individual components, in particular of the pneumatic installation are not illustrated in this illustration for reasons of clarity and simplification.
  • FIG. 5 is a schematic illustration of a vehicle 2000 —in this case, in the form of a passenger vehicle—having a compressed air supply installation 1000 and a pneumatic installation 600 .
  • vehicle 2000 in this case, in the form of a passenger vehicle—having a compressed air supply installation 1000 and a pneumatic installation 600 .
  • the passenger vehicle 2000 which is illustrated here by way of example for this reason, without limiting the applicability to trucks or other utility vehicles, has four wheels 801 , 802 , 803 and 804 , of which the two front wheels are shown here as a result of the cross-sectional illustration.
  • the pneumatic installation 600 has four pneumatic springs 601 , 602 , 603 and 604 , of which the two front pneumatic springs are shown here as a result of the cross-sectional illustration similarly to the wheels.
  • the pneumatic springs 601 , 602 , 603 and 604 which are each associated with the wheels 801 , 802 , 803 and 804 are supplied with compressed air as part of the pneumatic installation 600 by the compressed air supply installation 1000 .
  • the compressed air supply installation 1000 is connected in a fluid-conveying manner via the screen 570 to the components of the pneumatic installation 600 , in this case the pneumatic springs 601 , 602 , 603 and 604 illustrated here.
  • the compressed air supply installation 1000 is shown in this illustration in a highly simplified manner so that only the compressed air store 560 and the compressor 400 can be seen.
  • the compressor 400 could be used additionally or alternatively independently of the compressed air supply installation in a modification which is not shown here.
  • the concept preferably provides the basis for a compressor arrangement which functions in an improved manner, in particular one which is compact and low in noise and vibrations. Furthermore, a reduction of forces and/or moments and in particular a reduction of the dynamic loads and vibrations which are connected with the forces and/or moments lead to a more protective operation which has a positive effect on the efficiency and service-life of the compressor arrangement.
  • the recitation of “at least one of A, B and C” should be interpreted as one or more of a group of elements consisting of A, B and C, and should not be interpreted as requiring at least one of each of the listed elements A, B and C, regardless of whether A, B and C are related as categories or otherwise.
  • the recitation of “A, B and/or C” or “at least one of A, B or C” should be interpreted as including any singular entity from the listed elements, e.g., A, any subset from the listed elements, e.g., A and B, or the entire list of elements A, B and C.
US16/757,773 2017-10-23 2018-09-05 Compressor assembly for operating a compressed air supply system, compressed air supply system, and vehicle Active US11041489B2 (en)

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DE102017009842.5A DE102017009842A1 (de) 2017-10-23 2017-10-23 Verdichteranordnung zum Betreiben einer Druckluftversorgungsanlage, Druckluftversorgungsanlage, Fahrzeug
DE102017009842.5 2017-10-23
PCT/EP2018/073809 WO2019081106A1 (de) 2017-10-23 2018-09-05 Verdichteranordnung zum betreiben einer druckluftversorgungsanlage, druckluftversorgungsanlage, fahrzeug

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DE102017009842A1 (de) * 2017-10-23 2019-04-25 Wabco Gmbh Verdichteranordnung zum Betreiben einer Druckluftversorgungsanlage, Druckluftversorgungsanlage, Fahrzeug
DE102018204713A1 (de) * 2018-03-28 2019-10-02 Robert Bosch Gmbh Seitenkanalverdichter für ein Brennstoffzellensystem zur Förderung und/oder Verdichtung von einem gasförmigen Medium
US11383071B2 (en) * 2020-03-10 2022-07-12 Long Xiao Tattoo device with motor having built-in motion conversion member

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US20200378377A1 (en) 2020-12-03
CN111247338A (zh) 2020-06-05
EP3701147B1 (de) 2021-07-28
CN111247338B (zh) 2022-04-08
WO2019081106A1 (de) 2019-05-02
EP3701147A1 (de) 2020-09-02

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